Movement stage for a hydraulic shock absorber and shock absorber with the movement stage

ABSTRACT

A movement stage for a hydraulic shock absorber has a damping volume and a stage throttle with a valve disk, an analogue piston, and an elastic biasing means supported on the analogue piston and on the valve disk. The valve disk has a pressure surface defining a portion of the surface of a disk valve arranged upstream of an entry edge of a disk valve seat. The analogue piston has a pressure surface facing away from the biasing means. The valve disk pressure surface and the analogue piston pressure surface are impinged by damping fluid flowing out of the damping volume as the shock absorber moves in a movement direction. The analogue piston pressure surface is larger than the valve disk pressure surface when projected in the closing direction of the disk valve so that the analogue piston is displaced and the bias of the valve disk increases.

CROSS REFERENCE TO RELATED APPLICATIONS

This application is a continuation application of U.S. patentapplication Ser. No. 15/159,522 filed on May 19, 2016, which is acontinuation application of international patent applicationPCT/EP2014/074854, filed Nov. 18, 2014, designating the United Statesand claiming priority from German application 10 2013 112 739.8, filedNov. 19, 2013, and the entire content of these applications isincorporated herein by reference.

TECHNICAL FIELD

The invention relates to a movement stage for a hydraulic shock absorberand the shock absorber with the movement stage.

BACKGROUND

A damping strut in combination with a spring strut utilized as a wheelsuspension for a bicycle is known. The damping strut has a hydraulicshock absorber that is a monotube shock absorber filled with a dampingfluid. A damping piston is supported in the monotube shock absorber suchthat it can be displaced longitudinally for displacing the dampingfluid. The damping piston has a plurality of damping openings. Duringretraction and extension of the damping strut, the damping piston isdisplaced in the monotube shock absorber, and the damping fluid isdisplaced by the damping piston such that the damping fluid flowsthrough the damping openings. The flow of the damping fluid in themonotube shock absorber, in particular through the damping openings, islossy, and results in a damping force that counteracts the movement ofthe damping strut.

Requirements in particular with respect to the strength and the dynamicof the damping force are applied to the damping strut during occurrenceof diverse riding situations with the bicycle, wherein a ride with thebicycle with high safety and with high comfort is supposed to be enabledby the requirements. Thus, it is desirable, when, for example, thebicycle is driven over a high curbstone edge or a lower stone,independent of the stroke position of the damping strut being therebypresent, the damping force of the shock absorber is in both cases firstpossibly low and increases smoothly with a slight increase in thefollowing stroke course so that the highest damping force is reachedduring reaching a maximum of the obstacle, thus still before the maximumamplitude of the stroke excitation by the obstacle. At the beginning,the damping strut can be retracted fast over the obstacle by thedescribed damping force course, whereby the wheel can dodge the obstaclewell without transmitting an overly impact from the curbstone edge orthe stone to the frame of the bicycle and whereby the wheel is maximallydecelerated during reaching the maximum of the obstacle so that further(and therefore harmful) retraction of the wheel caused by the inertia ofthe unsprung masses is prevented, whereby a contact loss to the road isprevented. The safety as well as the comfort of the rider during ridingis therefore increased and the fluctuation of the wheel load of thesprung wheel is reduced, so that the tire-road contact is increased.

The stroke excitation is defined as the momentum that causes themovement of the damping strut during the influence duration of themomentum, that is, during the excitation duration. The stroke excitationmaximum is the maximum stroke height of a theoretical, barely dampeddamping strut, wherein the maximum stroke height is caused by thismomentum influence. The maximum of the obstacle is the maximum heightdifference of the obstacle in relation to the height level of the roadsurrounding the obstacle, wherein the maximum height difference has tobe overridden by the damping strut during rolling over the obstacle.

The rider of the bicycle generally performs a rhythmic weight shiftduring pedaling, whereby the bicycle is brought in a rocking movement.When the rider of the bicycle initiates an abrupt braking maneuver, thenodding momentum thereby acting on the vehicle's center of mass leads toa strong retraction of the damping strut of the front wheel andsimultaneously to a strong extension of the damping strut of the rearwheel. Pedaling induced rocking movements and braking induced retractionand extension movements of the damping strut are tendentiously perceivedas being disturbing and can even, when having a too large extends,become a safety risk for the rider. It is therefore further desirablethat the damping force possibly increases fast and very strong duringthese undesired shock absorber movements, whereby these strokeexcitations are attenuated by the damping strut still before the dampingstrut can retract far, so that a ride with high comfort and with highsafety is enabled.

SUMMARY

It is an object of the invention to provide a movement stage for ahydraulic shock absorber and the shock absorber with the movement stage,wherein a safe and comfortable ride is enabled with the shock absorberin a vehicle.

The object is solved by providing a movement stage for a hydraulic shockabsorber including: a damping volume filled with an incompressibledamping fluid; a stage throttle having a disk valve with a valve disk,an analogue piston and an elastic biasing means configured for biasingthe valve disk in a closing direction of the disk valve; the stagethrottle being arranged so that the damping fluid flows through thestage throttle in a direction opposite to the closing direction of thedisk valve as the shock absorber moves in at least one movementdirection; the disk valve being configured to generate a shock absorberresistance force; the stage throttle being supported on the analoguepiston and on the valve disk to elastically couple the analogue pistonvia the biasing means with the disk valve; the valve disk having a valvedisk pressure surface; the valve disk pressure surface being a portionof a surface of the disk valve that is arranged upstream of an entryedge of a disk valve seat; the analogue piston having an analogue pistonpressure surface; the analogue piston pressure surface being arranged toface away from the biasing means; the valve disk pressure surface andthe analogue piston pressure surface being impinged by the damping fluidflowing out of the damping volume during the movement of the shockabsorber in the at least one movement direction; and, the analoguepiston pressure surface being larger than the valve disk pressuresurface when projected in the closing direction of the disk valve sothat a bias of the valve disk is increased when the analogue piston isdisplaced towards the biasing means as the shock absorber moves in theat least one movement direction.

According to an aspect of the invention, the movement stage for ahydraulic shock absorber has a damping volume that is filled with anincompressible damping fluid. The movement stage according to the aspectof the invention includes a stage throttle that has a disk valve with avalve disk. The damping fluid flows through the stage throttle oppositeto the closing direction of the disk valve as the shock absorber movesin one of the movement directions, whereby a shock absorber resistanceforce is generated by the valve disk. According to an aspect of theinvention, the stage throttle includes an analogue piston and, forbiasing the valve disk in the closing direction of the disk valve, anelastic biasing means that is supported on the analogue piston and onthe valve disk, so that the analogue piston is elastically coupled withthe disk valve via the biasing means. According to an aspect of theinvention, the valve disk has a valve disk pressure surface that is aportion of the surface of the disk valve, which is arranged upstream ofthe entry edge of the disk valve seat. The analogue piston has ananalogue piston pressure surface arranged to face away from the biasingmeans, wherein the valve disk pressure surface and the analogue pistonpressure surface are impinged by damping fluid flowing out of thedamping volume during the movement of the shock absorber in at least onemovement direction and, projected in the closing direction of the diskvalve, the analogue piston pressure surface is larger than the valvedisk pressure surface, so that the analogue piston is displaced in thedirection of the biasing means as the shock absorber moves in at leastone movement direction and the bias force of the valve disk thereforeincreases.

The invention is based on the following observations: Despite completelydifferently high stroke excitation maxima, the excitation duration ofthe stroke excitation caused by different obstacles, for example by acurbstone edge or by a lower stone and the excitation duration of thedesired movements of the damping strut triggered thereby, areapproximately equally long. This is true in particular until thereaching of the respective obstacle maximum, or of the respective strokeexcitation maximum. The excitation duration of the stroke excitationchanges over the range of the typical ride velocities of the bicycleonly to a small extent and is considerably shorter than the oftenmultiple times longer excitation duration that is caused by rockingexcitations as well as by braking induced stroke excitations thattrigger undesired movements of the shock absorber. In contrast, if theamplitudes of the stroke excitations of the desired and undesired shockabsorber movements are compared with each other, no distinguishingquantitative feature between both groups can be recognized. The same istrue for the retraction or extension velocities of the damping strut.These relationships are revealed both during the retraction and duringthe extension of the shock absorber.

According to an aspect of the invention, the analogue piston pressuresurface projected in the closing direction of the disk valve is up tofour times larger than the valve disk pressure surface. The analoguepiston preferably includes an analogue piston counter surface that isfacing away from the analogue piston pressure surface and that isimpinged by the damping fluid that has already passed the disk valveseat during the movement of the shock absorber in the one movementdirection. Further, the analogue piston pressure surface and theanalogue piston counter surface projected in the closing direction ofthe disk valve are preferably equally large.

The elastic biasing means is preferably arranged between the analoguepiston and the valve disk, so that the elastic biasing means isspatially isolated from the damping fluid that has not yet passed thedisk valve seat during the movement of the shock absorber in themovement direction. According to another aspect of the invention, theanalogue piston lies on the disk valve such that the analogue piston canbe displaced and the analogue piston is sealed by damping fluid, thatis, sealed by a damping fluid seal.

The disk valve includes a valve shaft that has a shape of a hollowcylinder, wherein the valve disk is arranged outside the valve shaft,and the analogue piston is arranged in the valve shaft such that theanalogue piston can be displaced. The valve shaft has on its inner sidea protrusion, on which the biasing means is supported. The analoguepiston can preferably be brought in a first extreme position, in whichthe bias force that is brought from the analogue piston via the biasingmeans on the valve disk is minimal, or zero. According to a furtheraspect of the invention, the analogue piston can be brought in a secondextreme position, in which the bias force that is brought from theanalogue piston via the biasing means on the valve disk has a maximumvalue. The analogue piston is displaced during the movement from thefirst extreme position to the second extreme position, in particular inthe closing direction of the disk valve. It is hereby preferred that theanalogue piston lies in its second extreme position on a stop of themovement stage. The stop is attached in such a position that the valvedisk can still carry out its full valve stroke under elastic bias by thebiasing means. It is therefore required that a small remaining stroke ofthe biasing means is still available in this position, wherein theremaining stroke is at least as high as the complete valve stroke of thevalve disk.

According to an aspect of the invention, the movement stage has anon-return valve with a closing direction opposite to the closingdirection of the disk valve and a seat ring being concentricallyarranged around the valve shaft, wherein the disk valve seat is formedon a front side of the seat ring and the non-return valve seat is formedon the other side of the seat ring, so that the non-return valve isclosed during the open disk valve and the non-return valve is openduring the closed disk valve, whereby the non-return valve acts as acounter stage throttle to the stage throttle.

The biasing means is preferably a coil spring. According to anotheraspect of the invention, the biasing means is a gas spring. Theprotrusion is formed in a shape of a ring and the analogue piston has apiston shaft that extends through the opening of the protrusion and liesgas sealed on the protrusion, wherein a chamber is confined between theanalogue piston and the protrusion, wherein the chamber is filled withgas. According to a further aspect of the invention, the analogue pistonhas two piston heads that are held in a distance to each other by thepiston shaft, wherein the protrusion is arranged between the pistonheads, so that a first chamber and a second chamber are confined by thepiston heads and the protrusion, wherein the chambers are filled withgas. The piston shaft preferably has a connection recess, wherein, whenthe analogue piston is in such a position that the protrusion isarranged immediately neighbored to the connection recess, so that bothchambers are connected with each other in a gas conductive manner, thegas pressure equalizes in both chambers via the connection recess.

According to a further aspect of the invention, an alternative movementstage is provided that differs from the preceding movement stage in thatthe elastic biasing means is supported on the analogue piston and on asupport seat of the movement stage. The analogue piston pressure surfaceof the analogue piston is arranged to face away from the biasing means,and the valve disk pressure surface of the valve disk is a portion ofthe surface of the valve disk that is arranged upstream of the entryedge of the disk valve seat. The valve disk has a valve disk pistonsurface that is arranged to face away from the valve disk pressuresurface, wherein the valve disk pressure surface and the valve diskpiston surface and the analogue piston pressure surface are impinged bydamping fluid flowing out of the damping volume as the shock absorbermoves in the at least one movement direction, so that the biasing meansis coupled with the disk valve via the analogue piston and the dampingfluid impinged on the valve disk piston surface, and, projected in theclosing direction of the disk valve, the valve disk piston surface islarger than the valve disk pressure surface, so that the analogue pistonis displaced in a direction toward the biasing means and the bias forceof the valve disk therefore increases as the shock absorber moves in theat least one movement direction.

According to an aspect of the invention, projected in the closingdirection of the disk valve, the valve disk piston surface is up to fourtimes larger than the valve disk pressure surface. According to anotheraspect of the invention, projected in the closing direction of the diskvalve, the analogue piston pressure surface and the valve disk pistonsurface are preferably equally large. It is furthermore preferred that,projected in the closing direction of the disk valve, the analoguepiston pressure surface and the analogue piston counter surface areequally large.

According to an aspect of the invention, the elastic biasing means isarranged between the analogue piston and the support seat, so that theelastic biasing means is spatially isolated from the damping fluid thathas not yet passed the disk valve seat as the shock absorber moves inthe at least one movement direction.

The analogue piston is arranged such that it can be displaced in ahollow cylinder borne in the casing of the shock absorber, wherein theanalogue piston is sealed by a damping fluid seal. The analogue pistoncan be brought in a first extreme position in the hollow cylinder,wherein the bias force that is brought from the analogue piston via thedamping fluid to the valve disk piston surface on the valve disk is zeroat a first extreme position. It is further preferred that the analoguepiston is moved to a second extreme position, at which the bias forcethat is brought from the biasing means via the analogue piston and thedamping fluid over the valve disk piston surface on the valve disk has amaximum value. The damping fluid seal of the analogue piston generates afriction force as the analogue piston moves from the first extremeposition to the second extreme position, wherein the friction forceincreases the bias force of the valve disk in closing direction of thedisk valve via the analogue piston and the damping fluid over the valvedisk piston surface. It is hereby preferred that the disk valve has apiston stump, wherein the valve disk is arranged on an outside of thepiston stump and the valve disk piston surface is arranged on a frontside of the piston stump. The hollow cylinder is confined by a side ofthe analogue piston pressure surface of the analogue piston by thepiston stump such that it can be displaced in the hollow cylinder andthe hollow cylinder is confined by a side of the analogue piston countersurface on the inner side of the support seat, on which the basing meansis supported.

According to an aspect of the invention, the movement stage includes anon-return valve with a closing direction opposite to the closingdirection of the disk valve and a seat ring arranged concentricallyaround the piston stump, wherein the disk valve seat is arranged on afront side of the seat ring and the non-return valve seat is arranged onanother front side of the seat ring, so that the non-return valve isclosed during the open disk valve and the non-return valve is openduring the closed disk valve, whereby the non-return valve acts as acounter stage throttle to the stage throttle.

According to an aspect of the invention, the biasing means is a coilspring. According to another aspect of the invention, the biasing meansis a gas spring, wherein the support seat is preferably formed in ashape of a ring and the analogue piston has a piston shaft that extendsthrough the opening of the protrusion and is arranged gas sealed on theprotrusion, wherein a chamber is confined between the analogue pistonand the support seat, wherein the chamber is filled with gas. It ispreferred that the analogue piston has two piston heads that are held ina distance to each other by the piston shaft, and wherein the supportseat is arranged between the piston heads, so that a first chamber and asecond chamber are confined by the piston heads and the support seat,wherein the chambers are filled with gas. It is furthermore preferredthat the piston shaft has a connection recess, wherein, when theanalogue piston is in such a position that the support seat is arrangedimmediately neighbored to the connection recess, both chambers areconnected with each other in a gas conductive manner, and the gaspressure equalizes in the both chambers via the connection recess.

The position is the first extreme position for both inventive andpreferred movement stages. Further, the stage throttle preferably has adamping fluid channel from the damping volume to the analogue pistonpressure surface and a counter channel from the analogue piston countersurface to the damping volume, wherein one of the channels or even bothhave a cross-section reduction, with which the displacement velocitiesof the analogue piston in relation to the movement velocities of theshock absorber are adjusted. According to an aspect of the invention,parallel to the cross-section reduction, a back flow bypass with a backflow valve is provided that is connected such that, when the bias forceof the valve disk increases via the biasing means by the analoguepiston, the back flow valve is in its closed condition and, when thebias force of the valve disk decreases via the biasing means by theanalogue piston, the back flow valve is in its open condition.

According to yet another aspect of the invention, the stage throttle hasan additional elastic biasing means, with which the valve disk is alwaysbiased in the closing direction of the disk valve. The disk valvepreferably has an access channel, with which at least one of thechambers can be accessed from the outside. It is hereby preferred thatthe access channel includes a pipe piece that is arranged perpendicularto the closing direction of the disk valve and is arranged with a firstlongitudinal end in the disk valve such that it can be pivoted and isarranged with its second longitudinal end in the casing of the shockabsorber such that it can pivoted.

According to an aspect of the invention, there is still so muchremaining stroke of the elastic biasing means present in the secondextreme position of the analogue piston that the valve disk can bebrought in its full open condition, whereby the valve disk is alwayselastically and flexibly biased.

According to another aspect of the invention, the stroke of the analoguepiston from its first extreme position to its second extreme position islarger than a complete valve stroke of the valve disk. This stroke ofthe analogue piston is particularly preferred at least four times largerthan the complete valve stroke of the valve disk.

According to yet another aspect of the invention, the elastic biasingmeans has in at least one range of the valve stroke (x) of the valvedisk a force-distance characteristic curve, wherein a first derivativeof the force-distance characteristic curve is substantially zero(F′=dF/dx≈0). It is thereby in particular preferred that the range ofthe valve stroke (x) corresponds to the complete valve stroke of thevalve disk.

The shock absorber according to an aspect of the invention has at leastone of the movement stages according to the various aspects of theinvention. The shock absorber may include two of the movement stages,wherein one of the movement stages is a compression stage and the othermovement stage is a rebound stage.

The bias of the valve disk is obtained with the biasing means. Since theanalogue piston is displaced in a direction relative to the biasingmeans as the shock absorber is moved, the bias of the valve disk can bedosed by the analogue piston. According to an aspect of the invention,the bias of the valve disk is dosed by the analogue piston such thatduring the retraction of the shock absorber the bias of the valve diskincreases at least in part.

The movement stage according to an aspect of the invention is providedwith the biasing means such that the valve stroke of the valve disk isgenerally much smaller than the stroke of the biasing means, whereby theforce-distance-characteristic curve of the bias of the valve disk by thebiasing means has substantially a constant value in the range of thevalve stroke (x), wherein a first derivative of theforce-distance-characteristic curve is substantially zero (F′=dF/dx≈0).A valve stroke of the valve disk is the movement distance of the valvedisk with respect to the valve disk seat, so that a valve openingresults between the valve disk and the valve disk seat. The maximum opencondition of the valve disk is the valve position, at which the valvestroke and therefore the valve opening are at a maximum.

The valve disk is therefore always elastically biased by the biasingmeans with the constant force-distance-characteristic curve, wherein thelevel of the bias is given by the analogue piston during the movement ofthe shock absorber. The intensity of the bias force from the biasingmeans to the disk valve is controlled by the analogue piston, whereinthe characteristic of the force-distance-characteristic curve of thebiasing means is unchanged at each point in time, whereby thecharacteristic of the force-distance-characteristic curve of the bias ofthe valve disk remains also unchanged. The biasing means can therebyinclude a linear or a progressive or a degressiveforce-distance-characteristic curve over its complete stroke. Thebiasing means acts on the valve disk only gradually and time delayed bythe analogue piston, in particular by using a cross-section reductioneither in the counter channel or in the damping fluid channel of theanalogue piston. The displacement of the analogue piston in a directiontoward the biasing means is caused since, projected in the closingdirection of the disk valve, the analogue piston pressure surface islarger than the valve disk pressure surface for the first alternativemovement stage and, projected in the closing direction of the diskvalve, the valve disk piston surface is larger than the valve diskpressure surface for the second alternative movement stage. The sizeratio of the involved surfaces results in a respective movement velocityof the analogue piston of the first movement stage according to anaspect of the invention. For the second alternative movement stage, themovement velocity is additionally influenced by the size ratio of theanalogue piston pressure surface projected in the closing direction ofthe disk valve in relation to the valve piston pressure surfaceprojected in the closing direction of the disk valve.

At different movement velocities of the shock absorber, the valve diskis arranged at different valve strokes due to the respective differentdisplacement effects of the damping fluid. Since theforce-distance-characteristic curve of the biasing means in the range ofthe valve stroke (x) is substantially constant over the valve stroke andthe first derivative of the force-distance-characteristic curve in therange of the valve stroke (x) is therefore substantially zero(F′=dF/dx≈0), the bias of the valve disk is thereby almost independentfrom its current valve stroke at each point in time of the movement,whereby, as a result, the damping force of the shock absorber is alsoindependent from the retraction velocity of the shock absorber at eachpoint in time seen individually.

The pressure of the damping fluid that is coming either from theascending pipe or from the damping volume that did not yet pass theentry edge of the disk valve seat of this valve disk, is therefore onlydependent from the position of the analogue piston. The bias of thebiasing means resulting therefrom is independent from the currentretraction velocity of the shock absorber. Since this pressure, reducedby an almost constant value when the cross-section reduction is present,is present also on the analogue piston pressure surface of the analoguepiston of this valve disk, the force that increasingly compresses theelastic biasing means of this valve disk, and therefore also themovement velocity of the analogue piston is also independent from thecurrent retraction velocity of the shock absorber. The time durationthat is required to raise the bias of the biasing means via the analoguepiston from the minimum to the maximum value and therefore to bias thevalve disk, is therefore also independent from the movement velocity ofthe shock absorber and therefore even at different stroke velocitycourses of the shock absorber always approximately equally long, wherebyin turn the retraction resistance force of the shock absorber isparticularly advantageous purely dependent on the retraction duration ofthe shock absorber always in the same manner.

A wheel of a bicycle is for example suspended on the frame of thebicycle with the shock absorber. For example, the bicycle drives towardsa curbstone edge. At a point in time, at which the wheel impinges on thecurbstone edge, a hard impact, thus a stroke excitation with a highamplitude within a particularly short duration, is transmitted from thecurbstone edge to the wheel and therefore to the shock absorber. Theshock absorber starts now with the retraction, wherein starting with theretraction, the analogue piston is displaced in a direction toward thebiasing means within a predetermined period of time. The bias of thevalve disk by the biasing means at the beginning of the retraction ofthe shock absorber corresponds to a minimum value in a first extremeposition of the analogue piston, independent from the strength of theimpact and in particular independent from the stroke position of theshock absorber currently being present at the start of the retraction,whereby, caused by the great strength of the impact, the retractionvelocity of the shock absorber is high. For example, an increase of thebias of the biasing means by the analogue piston and therefore of thebias of the valve disk of the shock absorber occurs only very graduallyover the retraction stroke of the shock absorber, since the shockabsorber is configured to perform a long retraction stroke within the(for each stroke excitation always equally long) period of time that isrequired by the analogue piston to move from the first to the secondextreme position and therefore to maximize the bias of the valve disk.The period of time can ideally be set such that the highest dampingforce is only reached when the obstacle maximum is reached by the shockabsorber. In contrast, if the period of time is chosen such that it hasnot elapsed when reaching the maximum retraction stroke on the obstaclemaximum, the maximum damping forces are not even obtained with suchobstacles, whereby a maximum comfort setting of the shock absorber isobtained with very hard and fast impacts.

The possibly complete absorption of the described obstacle is onlypossible since the valve disk has the opening characteristic curveaccording to an aspect of the invention, whereby it has a very highopening degree without which the bias of the valve disk therebyincreases during the particularly high current retraction velocity ofthe shock absorber, wherein the particularly high current retractionvelocity occurs for a short term during overriding the curbstone edge.The damping force of the disk valve at each point in time is thereforeindependent from the current, in this case very high retractionvelocity, whereby a hardening of the shock absorber is first completelyprevented and the damping strut resistance force is purely determined bythe already elapsed portion of the first period of time and the biasvalue K thereby transmitted by a bias regulator. The first period oftime is thereby simultaneously approximately always equally long despitethe high movement velocity of the shock absorber.

The overridden height difference during riding the wheel up thecurbstone edge is therefore compensated by the damping strut, wherebythe unevenness caused by the curbstone edge is well overridden andbarely perceived by a bicycle rider. During reaching the obstaclemaximum, the wheel is then already maximally decelerated, so that afurther, harmful retraction of the damping strut and therefore thewheel, and therefore a contact loss to the road are prevented.

Since the excitation duration of the shock absorber only varies asdescribed in a very limited manner for different obstacle types, inparticular until reaching its obstacle maxima, respectively strokeexcitation maxima, the shock absorber generates, caused by theaccordingly preset, always equally long time duration that the analoguepiston needs to be displaced from the first to the second extremeposition and therefore to raise the bias of the biasing means to itsmaximum value starting from the first impingement of the wheel on theobstacle, the highest damping force reliably only in the range of theseobstacle maxima—completely independent on how high its retractionvelocity is thereby on the respective obstacle type and which strokeamplitudes it thereby reaches.

In contrast, the shock absorber with the movement stage behavesdifferently, when an undesired movement with a long enduring strokeexcitation occurs, as it is generated in a typical manner, for example,during pedaling or during a braking process initiated by the rider. Afast increase of the bias of the biasing means over the stroke of theshock absorber immediately occurs, since it is only enabled for the longretracting shock absorber in the (always equally long) time durationthat the analogue piston needs to move from the first to the secondextreme position and therefore to elastically maximal bias the valvedisk to perform a very short retraction stroke relative to the maximumamplitude of the stroke excitation. Higher damping forces are thereforebuilt up already at the beginning of the stroke movement within afraction of the maximum stroke amplitude, and even considerably beforethe stroke excitation maximum, so that, for example, a brake diving ofthe front wheel or a rhythmic weight shift of the bicycle rider duringpedaling are damped strongly and fast by the shock absorber byincreasing the damping force.

This is only possible, since the disk valve can generate sufficient andmost notably equally high damping forces during the thereby prevailing,rather low, but definitely strongly varying current retractionvelocities of the shock absorber, since the opening characteristic curveof the valve disk according to an aspect of the invention is independentfrom the current retraction velocity of the shock absorber due to itsbias being independent from the opening degree of the valve disk. Thedamping force is therefore purely determined by the already elapsed partof the time duration and the thereby obtained bias of the biasing meansby the analogue piston and the period of time is simultaneouslyapproximately always equally long, despite the different movementvelocities of the shock absorber.

The described behavior of the shock absorber according to an aspect ofthe invention is particularly advantageous, when the front wheel of thebicycle impinges on a large obstacle like the curbstone edge during thebeginning of a long enduring stroke excitation, for example, during astrong braking process, thus during a very strong increase of thedamping force in relation to the retraction stroke. The opening degreeof the always elastically and therefore flexibly biased valve diskimmediately increases without further biasing the biasing means, wherebysimultaneously and nearly free of delay, the retraction stroke performedby the shock absorber becomes longer, while the analogue piston isdisplaced in the direction of its second extreme position within the(for each stroke excitation always equally long) period of time, wherebyan increase of the damping force immediately flattens over theretraction stroke of the shock absorber. The shock absorber thereforereleases more retraction stroke for the occurring obstacle nearly freeof delay, whereby it can be absorbed substantially better. If theobstacle is overridden during the further occurring braking process,without that the maximum damping force is thereby reached, the increasegradient of the damping force course is immediately afterwards set upover the further retraction stroke of the shock absorber, whichprevailed before the impingement of the wheel on the curbstone edge,whereby the brake diving that would now result is prevented.

As soon as the retraction phase of the shock absorber has ended, theanalogue piston of the described compression stage begins to displaceback in a direction toward the first extreme position. This is achieved,on the one hand, by the now relaxing biasing means that can now displacewith its reset force the analogue piston that became pressure-free onits analogue piston pressure surface and, on the other hand, as soon asthe extension of the shock absorber has begun, additionally by thepressure of the damping fluid that has not yet passed the entry edge ofthe disk valve seat of the now active rebound stage, wherein thepressure acts on the analogue piston counter surface of the compressionstage in the same direction as the biasing means. Besides, the back flowvalve opens and so bridges the cross-section reduction, whereby thecross-section reduction becomes ineffective in its delaying function,whereby the reset duration that the analogue piston requires to movefrom the second to the first extreme position is only a fraction of theperiod of time that is necessary in a reverse direction.

As soon as a new retraction of the shock absorber occurs, the analoguepiston of the compression stage is reset in its first extreme positionby this fast reset, so that the bias of the disk valve and therefore thedamping force is again minimal, in particular zero. The damping forcecourse is therefore reset to its minimum value at a new start of theretraction mostly independent from the stroke position of the shockabsorber being present at the start of the retraction. This is of vitalimportance, since the shock absorber in operation, when the wheel dampedby the shock absorber rolls over an uneven ground contour, is always inanother stroke positions, whereby the shock absorber is also always inanother stroke position, when the shock absorber is retracting by astroke excitation.

The same function manners are true in the extension phase analogue forthe rebound stage of the shock absorber according to another aspect ofthe invention, when the movement stage is used as rebound stagethrottle.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention will now be described with reference to the drawingswherein:

FIG. 1 is a cross-section view of the shock absorber with the firstalternative movement stage utilized as a compression stage according toan example embodiment of the invention;

FIG. 2 is a more detailed view of a shock absorber cylinder shown inFIG. 1 according to an example embodiment of the invention;

FIG. 3 is an extract of the cross-section view of FIG. 1;

FIG. 4 shows an extract of a cross-section illustration of the shockabsorber with two first alternative movement stages according to anexample embodiment of the invention, in which one movement stage is acompression stage and another movement stage is a rebound stage;

FIG. 5 is an extract of a cross-section view of a shock absorber withthe first alternative movement stage according to a second exampleembodiment of the invention configured as a compression stage;

FIG. 6 shows a disk valve according to an example embodiment of theinvention;

FIG. 7 shows another disk valve according to an example embodiment ofthe invention;

FIG. 8 is an extract of a cross-section view of the shock absorber withthe second alternative movement stage configured as a compression stageaccording to the first example embodiment of the invention;

FIG. 9 is an extract of a cross-section view of the shock absorber withthe second alternative movement stage configured as a compression stageaccording to a second example embodiment of the invention;

FIG. 10 shows different stroke excitations of the shock absorber withspecific excitation durations, stroke amplitudes and stroke velocities,according to an example embodiment of the invention; and,

FIG. 11 shows characteristic curves of the damping force of the shockabsorber over the retraction stroke, when the shock absorber is exposedto stroke excitations shown in FIG. 10, according to an exampleembodiment of the invention.

DESCRIPTION OF EXEMPLARY EMBODIMENTS

In FIGS. 1 to 3, a shock absorber 1 is shown. The shock absorber 1 has ashock absorber cylinder 2. A damping volume 3 is provided in the shockabsorber cylinder 2, wherein the damping volume 3 is filled with adamping fluid 4, in particular with damping oil. A shock absorber piston5 is arranged such that it can be displaced longitudinally in thedamping volume 3, wherein the shock absorber piston 5 can be operatedfrom outside the shock absorber cylinder 3 by a piston rod 6. If theshock absorber piston 5 is displaced longitudinally in the shockabsorber cylinder 2 so that the piston rod 6 extends into the dampingvolume 3, the shock absorber 1 is retracted, wherein the retractiondirection is indicated in FIG. 1 with an arrow 7.

The damping volume 3 is divided in two halves by the shock absorberpiston 5, wherein during the displacement of the shock absorber piston 5one half of the damping volume 3 becomes smaller and another half of thedamping volume 3 becomes correspondingly larger. A damping opening 8 isprovided in the shock absorber piston 5, wherein the displaced dampingfluid 4 can flow from the one half of the damping volume 3 to the otherhalf of the damping volume 3 through the damping opening 8. Since thethrough flowing of the damping opening 8 generates losses in the dampingfluid flow, a respective shock absorber resistance force results,wherein the shock absorber resistance force counteracts the movement ofthe shock absorber piston 5.

At different stroke positions of the shock absorber piston 5, the pistonrod 6 extends differently long in the damping volume 3, whereby anaccordingly unequal displacement of the damping fluid 4 by the pistonrod 6 is involved. The shock absorber 1 has a compensation volumereservoir 9 for the compensation of this unequal displacement effect ofthe piston rod 6, wherein a compensation piston 10 is arranged in thecompensation volume reservoir 9 such that it can be displacedlongitudinally. An entry opening 11 is provided in the shock absorbercylinder 2 and an exit opening 12 is provided in the compensation volumereservoir 9, wherein the damping fluid 4 is channeled in during theretraction of the shock absorber 1 in the retraction direction 7 and ischanneled out during the extension against the retraction direction 7through the openings 11, 12 according to the displacement effect of thepiston rod 6 by displacing the compensation piston 10. The compensationpiston 10 is impinged on its side that faces away from the damping fluid4 by a pressurized gas cushion, so that the damping fluid 4 is alwaysexposed to a hydrostatic bias pressure. An ascending pipe 13 arranged inthe damping volume 3 extends from the compensation volume reservoir 9through the shock absorber piston 5 to the half of the damping volume 3that is the other half to the half in which the entry opening 11 isprovided. The ascending pipe 13 extends through the shock absorberpiston 5, so that the shock absorber piston 5 can be displacedlongitudinally along the ascending pipe 13. The ascending pipe 13 has anopening in the half of the damping volume 3, to which the piston rod 6extends, so that the damping fluid 4 can flow from the one half of thedamping volume 3 to the other half of the damping volume 3 through theentry opening 11 via the compensation volume reservoir 9 and theascending pipe 13.

In FIGS. 1 and 3, a compression stage 14 is illustrated a firstalternative movement stage according to a first example embodiment ofthe invention. The compression stage 14 is formed by a stage throttle 15that is arranged between the entry opening 11 and the exit opening 12.The amount of the damping fluid 4 that flows from the one half of thedamping volume 3 to the other half of the damping volume 3 flows throughthe stage throttle 15 a the shock absorber 1 moves. The flowing of thedamping fluid 4 involves flow losses, so that the shock absorberresistance force is also determined by the flow conditions prevailing inthe stage throttle 15.

The stage throttle 15 has a disk valve 16 that is built in the shockabsorber 1 such that the disk valve 16 is in an open condition andtherefore flown through by the damping fluid 4 during a retraction ofthe shock absorber 1 in the retraction direction 7, it is in a closedcondition and therefore not flown through by the damping fluid 4 duringthe extension of the shock absorber 1 opposite to the retractiondirection 7. The disk valve 16 has a valve disk 17 that is arranged inthe shock absorber 1 such that it can be displaced longitudinally on avalve shaft 18. The valve disk 17 is moved in its closing direction 19until the valve disk 17 lies on a disk valve seat 21 of the disk valve16 in order to bring the disk valve 16 in its closed condition. In orderto bring the disk valve 16 from the closed condition in its opencondition, the valve disk 17 is raised from the disk valve seat 21opposite to the closing direction 19, whereby a through flow opening isformed between the disk valve seat 21 and the valve disk 17, wherein thedamping fluid 4 flows through the through flow opening during theretraction of the shock absorber 1. The position of the through flowopening of the disk valve 16 marks an entry edge 22 of the disk valveseat 21, wherein the significant pressure drop arises on the entry edge22 during the through flowing of the through flow opening of the diskvalve 16 by the damping fluid 4. The portion of the damping fluid 4 thatis located upstream of the entry edge 22 has therefore a total pressurethat is higher by the pressure drop on the entry edge 22 than theportion of the damping fluid 4 that is located downstream of the entryedge 22 and has already passed the entry edge 22. The portion of thesurface of the valve disk 17 that is impinged upstream of the entry edge22 by the damping fluid 4 flown out of the damping volume 3 is denotedas valve disk pressure surface 20.

The valve shaft 18 is formed as a hollow cylinder, wherein the valvedisk 17 is attached on an outside of the valve shaft 18. Inside of thevalve shaft 18, a protrusion 23 extends radial from the valve shaft 18,wherein the protrusion 23 is arranged on the height of the valve disk17. The protrusion 23 is formed in a shape of a ring, so that an openingis formed by the protrusion 23 in the center around the longitudinalaxis of the valve shaft 18, wherein an analogue piston 24 is arranged inthe opening such that it can be displaced along the longitudinal axis ofthe valve shaft 18. The analogue piston 24 is formed in the manner of adouble hammer head and has a first piston head 29 and a second pistonhead 30, wherein the piston heads 29, 30 are held in a distance to oneanother by a piston shaft 34 that is arranged between the piston heads29, 30. The piston shaft 34 is engaged with the opening formed by theprotrusion 23, wherein, seen in the closing direction 19 of the diskvalve 16, the first piston head 29 is arranged on the other side of theprotrusion 23 and the second piston head 30 is arranged on this side ofthe protrusion 23. The piston heads 29, 30 are arranged on the innerside of the valve shaft 18 such that they can be displacedlongitudinally and are sealed to the valve shaft 18 with a damping fluidseal 37. A first chamber 31 is formed between the first piston head 29and the protrusion 23 and a second chamber 32 is formed between thesecond piston 30 and the protrusion 23, wherein the chambers 31, 32 arefilled with a gas 36. A gas seal 38 is provided on the side of theprotrusion 23 facing towards the valve shaft 18, wherein the firstchamber 31 is sealed in a gas sealed manner from the second chamber 32by the gas seal 38. Further, a connection recess 33 is arranged in thepiston shaft 34, wherein, when the analogue piston 24 is in a firstextreme position, the gas seal 38 is bridged via the connection recess33, so that the first chamber 31 is connected in a gas conductive mannerwith the second chamber 32 via the connection recess 23. A bias forcecan be brought on the valve disk 17 via the protrusion 23 because of thedifferent gas pressures in the chambers 31, 32, so that the chambers 31,32 act as a gas spring 35.

The first piston head 29 has a side facing away from the first chamber31, wherein the side is denoted as an analogue piston pressure surface25. The second piston head 30 has a side facing away from the secondchamber 32, wherein the side is denoted as an analogue piston countersurface 27. The shock absorber 1 has a damping fluid channel 44 thatguides the damping fluid 4 from the entry opening 11 upstream of theentry edge 22 to the analogue piston pressure surface 25. Further, theshock absorber 1 has a counter channel 28 that guides damping fluid 4from upstream of the entry edge 22 to the analogue piston countersurface 27. Since the analogue piston pressure surface 25 and theanalogue piston counter surface 27 are arranged to face away from eachother and since the analogue piston counter surface 27 is impinged bydamping fluid 4 that has already passed the entry edge 22 of the diskvalve seat 21, and since the analogue piston pressure surface 25 isimpinged by the damping fluid 4 that has not yet passed the entry edge22 of the disk valve seat 21, the pressure difference that arises on thedisk valve seat 21 during flowing through of the disk valve 16 acts onthe analogue piston 24.

The shock absorber 1 further includes a stop 49 that is fixed on theshock absorber cylinder 2, wherein the analogue piston 24 is arranged onthe stop 49, when the analogue piston 24 is in a second extremeposition. The stop 49 is particularly preferred arranged in such aposition that the valve disk 17 in the second extreme position of theanalogue piston 24 can still perform its complete valve stroke under anelastic bias by the biasing means 35, 43. It is therefore required thatin this position a remaining stroke of the biasing means 35, 43 is stillavailable, wherein the remaining stroke is at least as high as the valvestroke of the valve disk 17. In the second extreme position, theanalogue piston 24 is displaced in the valve shaft 18 such that the gasseal 38 is no longer bridged by the connection recess 23 and thepressure in the first chamber 31 is larger than in the second chamber32, wherein the bias force acting from the gas spring 35 on the valvedisk 16 has a maximum value. In contrast thereto, in the first extremeposition of the analogue piston 24, the first chamber 31 is connectedwith the second chamber 32 via the connection recess 33, so that thesame gas pressure prevails in both chambers and the bias force actingfrom the gas spring 35 on the valve disk 17 is therefore zero.

Projected in the closing direction 19 of the disk valve 16, the analoguepiston pressure surface 20 is larger than the valve disk pressuresurface 25, so that a movement of the analogue piston 24 from the firstextreme position in the second extreme position is initiated during theretraction of the shock absorber 1 in the retraction direction 7,wherein the bias of the valve disk 17 by the biasing means 35, 43remains always elastic, since the elastic biasing means 35, 43 alwayscomprises a remaining stroke also in the second extreme position of theanalogue piston 24, wherein the remaining stroke is at least as high asthe complete valve stroke of the valve disk 17. According to theembodiment shown in FIGS. 1 and 3, the ratio of the analogue pistonpressure surface 25 to the valve pressures surface 20 is 1.8.

The damping fluid seal and the gas seal 38 are formed as slip rings, inparticular as O-rings. The damping fluid 4 is sealed against the gas 36by the damping fluid seal 37, whereas the gas 36 of the first chamber 31is sealed against the gas 36 of the second chamber 32 by the gas seal38. Therefore, the contact pressure of the gas seal 38 against the innerside of the protrusion 23 is higher than the contact pressure of thedamping fluid seal 37 against the inner side of the valve shaft 18.During breaking free of the analogue piston 24 during its movement fromthe first extreme position to the second extreme position, the staticfriction on the damping fluid seal 37 and the gas seal 38 has to beovercome. Since the analogue piston 24 is displaced in the closingdirection 19 of the disk valve 16 during this movement, the breakingfree force of the analogue piston 24 lying on the valve disk 17 acts inthe closing direction 19 of the disk valve 16. The valve disk 17 istherefore pressed on the disk valve seat 21 by the analogue piston 24immediately at the start of the retraction of the shock absorber 1,whereby the disk valve 16 is held in a stable position in particularwith the minimum bias of the valve disk 17 being present at the start ofthe retraction of the shock absorber 1. Otherwise, the valve disk 17would run into danger to be raised due to the low bias at the start ofthe retraction of the shock absorber 1, respectively to vibrateuncontrollably, whereby a pressure rise on the valve disk 17 initiatingthe movement stage could even not occur sufficiently and the analoguepiston 24 would therefore not be displaced in direction of the biasingmeans. This is in particular true, if the breaking free forces andfriction forces of the seals 37, 38 of the analogue piston 24 would bedirected in the opening direction of the valve disk.

Since the elastic biasing means 35, 43 is spatially isolated from thedamping fluid 4 that has not yet passed the entry edge 22 of the diskvalve seat 21 together by the analogue piston 24 and by the valve disk17, a biasing means 35, 43 is sufficiently long and therefore has a longstroke in shape of, for example, the shown coil spring or gas spring.The biasing means 35, 43 has, for example, a stroke that is larger thanthe complete valve stroke of the valve disk 17 or the biasing means 35,43 has by its length a force-distance-characteristic curve that issubstantially constant over the valve stroke in the range of the valvestroke. A first derivative of the force-distance-characteristic curve issubstantially zero (F′=dF/dx≈0) in the range of the valve stroke, andcan be employed in the first place, since these biasing means cannotensure the spatial separation of the portion of the damping fluid 4 thathas not (or not yet) passed the entry edge 22 of the disk valve seat 21from the portion of the damping fluid 4 that has already passed theentry edge 22 of the disk valve seat 21 alone due to their geometricshape. But this is necessary for a pressure rise on the disk valve 17.Thus, the elastic biasing means 35, 43 further remains shielded from thepressure difference of this both portions of the damping fluid, wherebythe elastic biasing means 35, 43 is not exposed to a further force thanby the analogue piston 24, whereby it remains particularly advantageousalways unchanged in its characteristic according to an exampleembodiment of the invention.

An access channel 39 ends in the first chamber 32, wherein a pipe piece40 is inserted in the access channel 39, wherein the pipe piece 40 hason its longitudinal ends a respective tilt seal 41 (see FIGS. 6 and 7).The access channel 39 extends in the shock absorber cylinder 2 with itsfirst portion and in the valve disk 17 with its second portion, so thatthe both portions of the access channel 39 are moved relative to eachother during a movement of the valve disk 17. Both portions are bridgedby the pipe piece 40, wherein the pipe piece 40 is supported in theaccess channel 39 by the tilt seals 41 such that it can tilt. The accesschannel 39 is closed towards the outside by a pressure adjustment screw42, wherein a volume change of the access channel 39 can be set by anoperation of the pressure adjustment screw 42. The size of the commonvolume that is formed by the first chamber 32 together with the accesschannel 39 can therefore be changed by the pressure adjustment screw 42.The level of the pressure in the common volume and the size of thecommon volume determine the characteristic of the gas spring 35 andtherefore also the damping force of the movement stage. This can becarried out, as shown, manually by the pressure adjustment screw 42 onthe shock absorber or, for example, remote controlled by the rider onthe handlebar of the bicycle, for example in form of a riding experienceswitch, or also automatically, for example, controlled by a sensorsystem-control electronics-actuator system, based on storedcharacteristic maps and characteristic lines and dependent on diverseinfluence variables like the riding velocity of the bicycle, the wheelor frame accelerations of the bicycle, the overdriven ground profile, alongitudinal inclination of the bicycle, et cetera.

A cross-section reduction 45 is built in the damping fluid channel 44,wherein the cross section reduction 45 is furthermore provided with aback flow valve 46 and a back flow bypass 47. The cross-sectionreduction 45 becomes active when the damping fluid 4 flows from theentry opening 11 through the damping channel 44 to the analogue pistonpressure surface 25. The pressure rise on the analogue piston pressuresurface 25 is therefore reduced, whereby the movement velocity of theanalogue piston 24 is reduced. The back flow valve 46 gets into its openposition during the extension of the shock absorber 1, whereby the backflow bypass 47 is laid open, so that the cross-section reduction 45 ismade effectless and the damping fluid 4 can flow from the analoguepiston pressure surface 25 possibly low of losses and therefore fast viathe entry opening 11 back in the damping volume 3. The time duration ofthe movement of the analogue piston can be set by switching betweendifferent large cross-section reductions 45, for example, by a revolvernozzle (not shown) or by a cross-section reduction 45 that is adjustablein its effective cross-section (not shown). This can be carried outmanually on the shock absorber or, for example, remote controlled by therider on the handlebar of the bicycle, for example by using a ridingexperience switch, or also automatically, for example, controlled by asensor system-control electronics-actuator system, based on storedcharacteristic maps and characteristic lines and dependent on diverseinfluence variables like the riding velocity of the bicycle, the wheelor frame accelerations of the bicycle, the overdriven ground profile,the longitudinal inclination of the bicycle, et cetera.

Further, according to an example embodiment of the invention, an extraspring 48 is provided that is supported on the shock absorber cylinder 2and on the valve disk 17, wherein the valve disk 17 is biased in itsclosing direction by the extra spring 48. The disk valve 16 has asupport ring 51 that is centrically arranged around the axis of thevalve disk 17. The disk valve seat 21 is formed on one front end of thesupport ring 51, so that the inner edge forms the entry edge 22 of thedisk valve seat 21 on the respective side of the support ring 51. Anon-return valve seat 52 is arranged facing away from the respectivefront end, wherein a non-return valve 50 is arranged on the non-returnvalve 52, wherein the non-return valve 50 is formed by a ring disk thatis biased with a spring. A sealing of the support ring 51 against theshock absorber cylinder 52 is achieved by the ring disk, wherein thenon-return valve 50 is in its closed position during the retraction ofthe shock absorber 1 and in its open position during the extension ofthe shock absorber 1.

The shock absorber 1 shown in FIG. 4 has a compression stage 14 and arebound stage 53 interconnected in parallel to the compression stage 14,wherein the rebound stage 53 is identically constructed as thecompression stage 14, whereas the rebound stage 14 is built in the shockabsorber 1 such that the rebound stage 53 has the same functionalityduring the extension of the shock absorber 1 as the compression stage 14during the retraction of the shock absorber 1. The shock absorber 1shown in FIG. 4 is retracting. The rebound stage is damping. The largearrow in the damping volume 3 shows the movement direction of thedamping piston 5. The small arrows in the piping of the movement stagesshow the current flow of the damping fluid 4 during an active reboundstage 53. The analogue piston 24 of the compression stage 14 has alreadymoved back to its first extreme position, that is, the starting positionbefore the next retraction process. During the shown retraction processof the shock absorber 1, the elastic biasing means 35, 43 is maximallyrelaxed, whereas the analogue piston 24 of the rebound stage 53 is onits way to its second extreme position. The elastic biasing means 35, 43is continually further biased, wherein also the bias force of the valvedisk 17 is also increased against the disk valve seat 21. The movementstages of the rebound stage 53 and the compression stage 14 areadvantageously coupled with each other, as shown in FIG. 4, so that thedamping fluid 4 that (flowing from the damping volume 3) has not yetpassed the entry edge 22 of the disk valve seat 21 of the compressionstage 14 during the retraction of the shock absorber 1 which also actson the analogue piston counter surface 27 of the rebound stage 53. FIG.4 also shows that the damping fluid of the rebound stage 53, which(flowing from the ascending pipe 13) has not yet passed the entry edge22 of the disk valve seat 21 of the rebound stage during the retractionof the shock absorber 1, also acts on the analogue piston countersurface 27 of the compression stage 14. As a tenet, during a terrainride with always successive retraction and extension processes of theshock absorber 1, in addition to the reset force of the elastic biasingmeans 35, 43 of the current inactive movement stage (for example, therebound stage during the retraction), also the pressure of the dampingfluid 4, which is generated by the pressure drop on the valve disk 17 ofthe respective other, current active movement stage (for example, thecompression stage 15 during the retraction), is present on the analoguepiston counter surface 27 of the analogue piston 24 of the inactivemovement stage, and therefore displaces the analogue piston 24 in itsfirst extreme position, and therefore supports the elastic biasing means35, 43 of the current inactive movement stage with its relaxation untilit is reset in the first extreme position of the analogue piston 24 toits starting value. The small amount of the damping fluid 4 requiredthereto, which has not yet passed the entry edge 22 of the disk valveseat 21 of the current active movement stage, bypasses the disk valveseat 21 and the valve disk 17 of the current active movement stage. Thepiston rod 6 of the shock absorber 1 can therefore slightly move,although the valve disk 17 of the current active movement stage that isbiased by the extra spring 48 has not yet opened. The force for movingthe analogue piston 24 of the inactive movement stage in a direction toits first extreme position (and therefore for moving further the pistonrod 6) continually and smoothly increases, since the elastic biasingmeans of the movement stage increasingly relaxes, whereby itdecreasingly contributes to the reset force of the analogue piston 24,whereby also the pressure of the damping fluid 4 on the valve diskpressure surface 20 of the valve disk 17 of the current active movementstage continually smoothly increases until the current bias force of thebiasing means 35, 43 and of the extra spring 48 of the valve disk 17 isovercome and the disk valve opens. According to an example embodiment,the shock absorber 1 has a significantly improved response behavior toexcitations to tiniest unevenesses of the ground during an arbitrarychange between retraction and extension movement. This is particularlytrue, if it deals with vibrations, high frequent excitations andtherefore strokes of the piston rod 6 that are of such a short amplitudethat the valve disks 17 of both movement stages 14, 53 do not even open.

In FIG. 5, a second example embodiment of the first alternativecompression stage 14 is shown. The second example embodiment differsfrom the first example embodiment that is shown in FIGS. 1 and 3 in thata biasing spring 43 in a shape of a coil spring made of a flat materialis provided instead of the gas spring 35. The piston heads 29, 30 of theanalogue piston 24 are formed to a single piston head from which a pinis provided for lying on the stop 49 in the second extreme position.

In FIGS. 6 and 7, a gas conducting pipe piece 40 is shown with two tiltseals 41 and an access channel 39. The pipe piece 40 ensures a gasconductive connection of the first chamber 31 and/or the second chamber32 in the disk valve 16 that has an extremely low friction with the partof the access channel 39 of the pressure adjustment screw 42 that isattached in the access channel, wherein the access channel 39 isprovided in the shock absorber body, and with a filling valve (notshown) connected in a gas conductive manner with the channel 39, whilethe disk valve 16 moves up and down by its closing and openingmovements.

FIG. 6 shows a disk valve 16 which is connected only via a pipe piece 40with the shock absorber body in a gas conductive and movable manner.Ideally, the pipe piece is thereby slightly shifted to the axis of thedisk valve 16 towards the outside, as can be seen in the cross-sectionview of FIG. 6. The static pressure of the damping fluid 4 surrounds thedisk valve 16, wherein the pressure is, for example, brought up by thecompensation piston 10. The pressure has thereby to be always higherthan the pressure in the access channel 39 in order to prevent the pipepiece 40 from dropping out of its pockets in the disk valve 16 and inthe shock absorber body. The disk valve 16 with the front wall of itspocket is pressed against the spherical end of the pipe piece 41 by anoverpressure, whereby the pipe piece with its other spherical end ispressed on the front end of the pocket of the shock absorber body. Ifthe disk valve 16 opens, the position of the pipe piece 41 is slightlyinclined, whereby the disk valve 16 has to slightly rotate around itsaxis due to the overpressure, in order to remain pressed on thespherical end of the pipe piece 40, whereby it compensates theshortening of the pipe piece 40 due to its inclined position. The pipepiece 40 behaves like a connection rod that is tiltingthree-dimensionally, wherein the connection rod supports the rotationalmomentum of the disk valve 16 around its axis. The friction forcesgenerated by the tilt seals 41 are, in relation to the tilting directionof the pipe piece, almost negligible. Even when tightly seated, theforces on the slideway of the disk valve 16 in the shock absorber bodyare also minimal due the connection rod function of the pipe piece 40and the compensation rotation of the disk valve 16, whereby onlysmallest friction forces result in the opening and closing direction ofthe disk valve 16. In FIG. 7, two pipe pieces 40 are arranged oppositeto one another. The first chamber 31 is connected in a fluid conductivemanner to the shock absorber body by one of the pipe pieces. The secondchamber 32 is connected in a fluid conductive manner to the shockabsorber body by the second pipe piece 40. The pressure in one or inboth pipe pieces 40 becomes higher than the static pressure of thedamping fluid 4, since the disk valve 16 can be supported alternating onone of the both pipe pieces 40. It is not absolutely required that bothpipe pieces 40 are provided with an access channel 39 and the tilt seals41. Instead, only one pipe piece 40 is necessary for the gas conduction.

FIG. 8 shows the shock absorber 1 with a compression stage 14 of a firstexample embodiment of the second alternative movement stage. FIG. 9shows a shock absorber 1 with the compression stage 14 of a secondexample embodiment of the second alternative movement stage. Thecompression stage 14 of the second alternative movement stage accordingto the second example embodiment of the invention differs from thecompression stage 14 of the first alternative movement stage accordingto the first example embodiment of the invention in that the analoguepiston pressure surface 25 of the analogue piston 24 is arranged to faceaway from the gas spring 25, and respectively, from the biasing spring43, and the valve disk pressure surface 20 of the valve disk 17 covers aportion of the surface of the valve disk 17 that is arranged upstream ofthe entry edge 22 of the disk valve seat 21. Further, the valve disk 16of the compression stage 14 of the second alternative movement stageaccording to the second example embodiment of the invention has a valvedisk piston surface 55 that is arranged to face away from the valve diskpressure surface 20, wherein the valve disk pressure surface 20, thevalve disk piston surface 55, and the analogue piston pressure surface25 are impinged by the damping fluid 4 flowing out of the damping volume3 as the shock absorber 1 moves in the retraction direction 7. As aresult, the gas spring 25, and respectively the biasing spring 43, iscoupled with the disk valve 16 via the analogue piston 24 and thedamping fluid 4 that has not yet passed the entry edge 22 of the diskvalve seat 21 over the valve disk piston surface 55. The valve diskpiston surface 55, projected in the closing direction 19 of the diskvalve 16, is larger than the valve disk pressure surface 20, and sincethe analogue piston pressure surface 25 and the analogue piston countersurface 27 are arranged to face away from each other, since the analoguepiston counter surface 27 is impinged by the damping fluid 4 that hasalready passed the entry edge 22 of the disk valve seat 21, and sincethe analogue piston pressure surface 25 and the valve disk pistonsurface 55 are impinged by the damping fluid 4 that has not yet passedthe entry edge 22 of the disk valve seat 21, the pressure differencethat arises on the disk valve seat 21 during the flowing of the dampingfluid through the disk valve 16 acts on the analogue piston 24 and onthe valve disk piston surface 55. As a result, the analogue piston 24 isdisplaced in a direction toward the gas spring 25, and respectivelytoward the bias spring 43, during the retraction of the shock absorber 1and the bias force of the valve disk 17 thereby increases, wherein thebias of the valve disk 17 by the biasing means remains always elasticduring the movement of the analogue piston.

The shock absorber cylinder 2 of the compression stage 14 of the secondalternative movement stage according to the second example embodiment ofthe invention shown in FIGS. 8 and 9 has a hollow cylinder 56 that isfilled with damping fluid 4 that has already passed the entry edge 22 ofthe disk valve seat 22. The analogue piston 24 is arranged in the hollowcylinder 56 such that it can be displaced longitudinally. The valve disk17 has a piston stump 57 that is arranged in the hollow cylinder 56 suchthat it can be displaced longitudinally. For the compression stage 14 ofthe first example embodiment of the second alternative movement stageshown in FIG. 8, the protrusion 23 is arranged on the inner side of thehollow cylinder 56. Moreover, the compression stage 14 of the secondembodiment of the second alternative movement stage shown in FIG. 9 hasa support seat 54 that is arranged to face away from the piston stump57, wherein the biasing spring 43 is supported on the support seat 54.

The damping fluid seal 37 and the gas seal 38 are formed as slip rings,in particular as O-rings. The damping fluid 4 is sealed against the gas36 by the damping fluid seal 37, whereas the gas 36 of the first chamber31 is sealed against the gas 36 of the second chamber 32 by the gas seal38. During breaking free of the analogue piston 24 on its movement fromthe first extreme position to the second extreme position, the staticfriction on the damping fluid seal 37 and the gas seal 38 has to beovercome. Since the breaking free force of the analogue piston 24 in theclosing direction 19 of the disk valve 16 acts during this movement(transmitted from the analogue piston pressure surface 25 to the valvedisk piston surface 55 via the damping fluid 4 being present betweenthese two surfaces), the valve disk 17 is pushed by the analogue piston24 toward the disk valve seat 21 immediately at the start of theretraction of the shock absorber 1, whereby the disk valve 16 is held ina stable position, in particular with a minimal bias of the valve disk17 being present at the start of the retraction of the shock absorber 1.Otherwise, the valve disk 17 would run into danger to be raised due tothe low bias at the start of the retraction of the shock absorber 1,respectively to vibrate uncontrollably, whereby a pressure rise on thevalve disk 17 initiating the movement stage could even not occursufficiently and the analogue piston would therefore not be displaced inthe direction of the biasing means. This is in particular true, if thebreaking free forces and friction forces of the seals 37, 38 of theanalogue piston 24 act in the opening direction of the valve disk.

In contrast to the first alternative movement stage, the pressure of thedamping fluid 4 rises abruptly and therefore the damping force risesabruptly, when the analogue piston 24 of the second alternative movementstage reaches its stroke end, independent from the analogue piston 24being supported on the biasing means 35, 43 or on a stop 49, since thepressure of the damping fluid 4 that has not yet passed the entry edge22 of the disk valve seat 21 still acts on the valve disk pistonsurface. This makes a stop 49, having the same effect as the stop 49 ofthe first alternative movement stage, impossible. An equal effect as thestop 49 of the first alternative movement stage can be achieved for thesecond alternative movement stage by building a spring biased closedbypass valve, for example, in the shock absorber piston 5, wherein thebypass valve bridges the movement stage by overcoming the bias force ofthe bypass valve, as a desired maximum value of the pressure of thedamping fluid 4 (and therefore of the damping force of the movementstage) is reached, whereby the disk valve 16 is bridged, and whereby thedamping force no longer rises (not shown). A further possibility toachieve the equal effect is to interrupt the inflow of the damping fluid4 through the cross-section reduction 45 in the damping fluid channel44, as soon as the analogue piston 24 has reached the second extremeposition in which the analogue piston 24 is supposed to maximal bias thebiasing means 35, 43. This can, for example, be achieved by a controlrod (not shown) attached to the analogue piston 24, providedperpendicular to the analogue piston pressure surface 25 and concentricto the lateral surface of the analogue piston 25 and fed through thebore of the cross-section reduction 45, wherein the bore is alsoarranged in a concentric manner to the lateral surface of the analoguepiston 24. The effective cross-section of the cross-section reduction 45is therefore an annular gap formed by the bore of the cross-sectionreduction 45 and the thinner control rod fed through the bore. Thecontrol rod is thereby formed such that it includes a concentricthickening on its end facing away from the analogue piston, wherein thecontrol rod closes the cross-section reduction 45 with its end facingaway from the analogue piston, as the analogue piston 24 has reached thesecond extreme position. Therefore, the valve disk piston surface 55 issealed off from the further pressure rise of the damping fluid 4 thathas not yet reached the entry edge of the disk valve seat 22, wherebybias forces of the valve disk 17, and therefore the damping forces ofthe shock absorber 1, do not further rise. It is particularly preferredthat still so much remaining stroke in the biasing means 35, 43 ispresent at the second extreme position of the analogue piston 24 thatthe valve disk 17 can displace the analogue piston 24 over the dampingfluid enclosed between the valve disk piston surface 55 and the analoguepiston pressure surface 25 so far that the valve disk 17 is enabled toperform at least its complete valve stroke, whereby the valve disk 17remains elastically biased by the biasing means 35, 43 at the secondextreme position of the analogue piston 24.

Both, the bias of the described bypass valve and the position of theprotrusion 23, shown in FIGS. 4 and 5, or also the position of thethickening of the described control rod relative to the cross-sectionreduction 45 can be set manually on the shock absorber. They can also beremote-controlled by the rider on the handlebar of the bicycle, forexample in form of a riding experience switch. In addition, they can beautomatically controlled by a sensor system-control electronics-actuatorsystem based on stored characteristic maps and characteristic curves anddepending on diverse influence variables like the driving velocity ofthe bicycle, the wheel or frame accelerations of the bicycle, theoverridden terrain profile and/or the longitudinal inclination of thebicycle, et cetera.

Since the analogue piston pressure surface 25 and the analogue pistoncounter surface 27 of the analogue piston 24 are equally large, theposition of the analogue piston 24 in each stroke position of the shockabsorber 1 is independent from the hydrostatic bias pressure that istransmitted by the damping fluid 4 to the gas pressurized compensationpiston 10 (see description of FIG. 1) and it is therefore alsoindependent from the current stroke position of the shock absorber (thisis true for all embodiments of both alternative movement stages, shownin the FIGS. 1, 3, 4, 5). Only in this manner, the valve disk of theshown movement stages can be impinged by an always equal and very lowstart bias generated by the elastic biasing means 35, 43 during thestart of the retraction or the extension of the shock absorber 1, whichis necessary for the functioning of the movement stage, current strokeposition of the shock absorber 1. If the analogue piston counter surface27 and the analogue piston pressure surface 25 would be differentlylarge, either the analogue piston 24 can not return to each strokeposition of the shock absorber 1 in the start position, the firstextreme position, or to the existing bias of the analogue piston 24,which is caused by the above-described hydrostatic pressure of thedamping fluid 4. It would even have to be first overcome during thestart of the movement process of the shock absorber 1 before theanalogue piston 24 would be displaced, whereby a pressure rise on thevalve disk 17 initializing the movement stage would not even occursufficiently, whereby the analogue piston would not be displaced indirection of the biasing means 35, 43, whereby the bias force on thevalve disk 17 would not increase.

Since the elastic biasing means 35, 43 is simultaneously spatiallyisolated by the analogue piston 24 from the damping fluid 4 that has notyet passed the entry edge 22 of the disk valve seat 21, a sufficientlong and therefore long-stroke biasing means 35, 43 in a shape, forexample, of the shown coil spring or of a gas spring that has aforce-distance-characteristic line due to its length, theforce-distance-characteristic line is in the range of the valve strokesubstantially constant over the valve stroke and therefore the firstderivative of the force-distance-characteristic curve in the range ofthe valve stroke (x) is substantially zero (F′=dF/dx 0). Such a biasingmeans can not ensure the spatial separation of the portion of thedamping fluid 4 that has not yet passed the entry edge 22 of the diskvalve seat 21 from the portion of the damping fluid 4 that has alreadypassed the entry edge 22 of the disk valve seat 21 alone due to thegeometric shape of the biasing means. But this is necessary for thepressure rise on the disk valve 17. Further, the elastic biasing means35, 43 remains so shielded from the pressure difference of these twoportions of the damping fluid 4, whereby it is subjected to no furtherforce effect than by the analogue piston 24, whereby it remains alwaysunchanged in its characteristic according to an example embodiment ofthe invention.

In FIG. 10, the course of various stroke amplitudes of a theoretical,barely damped damping strut on the front wheel of a bicycle is shownover the time axis 58 during stroke excitations acting on the bicycle.The stroke excitations respectively include a stroke excitation maximum63. During a stroke excitation of the front wheel by obstacles 66, 67,this is during overriding the obstacle maximum by the front wheel, andtherefore at a maximum height difference of the obstacle to the level ofthe road directly surrounding the obstacle, a stroke excitation maximum63 follows only a short time later, since the barely damped dampingstrut further compresses shortly after the obstacle maximum is reacheddue to the mass inertia of the unsprung masses. Each stroke excitationcan be divided in two areas: an area before reaching the strokeexcitation maximum 56 that deals with a retraction excitation, and anarea after reaching the stroke excitation maximum 56 that deals with anextension excitation of the shock absorber. The gradient of the curvesrepresents the respective retraction/extension velocity of thetheoretical, barely damped damping strut over the stroke excitation. Thedifferent excitation duration of the stroke excitations can be seen inthe diagram: over the time axis 39 as the time ray from the intersectionpoint of the axes 58, 60 to the intersection point 65 of the curve ofthe respective stroke excitation with the time axis 58. It is marked bya reference sign if the respective stroke excitation triggers a desiredmovement 61 or an undesired movement 62 of the damping strut. It can beseen that stroke excitations by obstacles (curbstone edge 66; lowerstone 67) that trigger the desired movements 61 are substantiallyshorter than stroke excitations that are, for example, induced bybraking forces 68 or by pedaling 69 and that trigger undesired movements62. It is furthermore shown that the excitation duration over diverseobstacle types 59, 60, in particular until the reaching of the obstaclerespective stroke excitation maxima 63, is within a temporal very narrowrange 64. The reference sign 59 marks a line, wherein the intersectionof the line with the time axis 58 represents the end of the period oftime that is required by the analogue piston 24 of the shock absorber 1in order to move from the first to the second extreme position. Thepreset period of time therefore extends on the time axis 58 from theintersection point of the axes 58, 60 to this point. The intersectionpoint of the line 59 with the respective graphs of the strokeexcitations 66, 67, 68, 69 shows, in relation to the type of excitation,at which a current height of the excitation amplitude of the respectivestroke excitation the highest damping forces of the shock absorber 1 arereached according to an example embodiment of the invention. It can beclearly recognized that with the stroke excitations 66, 67 that triggerthe undesired stroke excitations 61, the highest damping forces arepresent already at a fraction of the maximum stroke amplitudes, evenlong before reaching the stroke excitation maxima 63, while during thestroke amplitudes of the desired damping strut movements 61, the dampingforces are reached only shortly before reaching the stroke excitationmaximum 63 and therefore on the obstacle maximum. If the end of the timeduration 59 can only be reached after reaching the stroke excitationmaximum 63, the maximum damping forces of the shock absorber 1 are noteven reached. Since the force-distance-characteristic line of thebiasing means 35, 43 is substantially constant in the range of the valvestroke, the first derivative in this range is substantially zero(F′=dF/dx≈0), and the damping force is independent from the respectivemovement velocity of the shock absorber 1, whereby also the pressuredrop of the damping fluid 4, which is generated on the valve disk 17, isindependent from the movement velocity and therefore also from the forceacting on the analogue piston 24, whereby the period of time that theanalogue piston 24 requires to move from its first extreme position toits second extreme position and therefore to maximally bias the biasingmeans 35, 43 is always equally long for all stroke excitations 66, 67,68, 69 and therefore its end 59 is reached always after the same timeafter the beginning of the respective stroke excitation 66, 67, 68, 69.

The gradients of the stroke excitations 67 and 68 are equally steep inranges, whereby also the retraction velocities of the undamped dampingstrut are almost identical in this ranges of the stroke excitations.Also the amplitudes of the stroke excitations 66 and 68 areapproximately equally high. It can therefore well be recognized thatneither the stroke amplitudes nor the movement velocities are suitablefor distinguishing desired and undesired stroke excitations of thedamping strut and accordingly for regulating the damping force. Theshock absorber is in its damping force particularly advantageousindependent from both the movement velocities and the stroke amplitudesas direct influence factors.

In FIG. 11, the course of the damping force 75 of the shock absorber 1is plotted over its retraction stroke 74, when the shock absorber 1 isexposed to the different stroke excitations shown in FIG. 10 startingfrom the beginning of the stroke excitation to the respective strokeexcitation maximum. The reference number 70 denotes the damping strutcourse over the stroke excitation 66 of the curbstone edge, thereference number 71 denotes the damping force course over the strokeexcitation 67 of the stone, the reference number 72 denotes the dampingforce course over the stroke excitation 68 during the braking process,and the reference number 73 denotes the damping strut course over thestroke excitation 69 by pedaling induced rocking. Undesired shockabsorber movements are triggered by stroke excitations 68, 69 triggerdamping force courses 72, 73 with particularly steep gradients, wherebymaximal damping forces are caused already during particularly smallretraction strokes.

Desired shock absorber movements that are triggered by the strokeexcitations 66, 67 having damping force courses 70, 71 with flatgradients, wherein the damping force courses 70, 71 smoothly risestarting from a minimal starting value. They reach their highest dampingforces at the respective obstacle maximum but at different retractionstrokes, whereby the shock absorber 1 always releases as much retractiondistance, as it is necessary for the complete absorption of thedifferently high obstacles. With the damping force course 70 over thecurbstone edge, the maximum damping force is not reached, since the timeduration that the analogue piston of the shock absorber requires to movefrom the first to the second extreme position is set such that it hasnot elapsed during reaching of the obstacle maximum, respectively of thestroke excitation maximum. The maximally reached damping force over thecurbstone edge is therefore smaller than the maximally reached dampingforce over the low stone, whereby a particular comfort setting of theshock absorber over particular hard and fast impacts is reached.

The functions are analogue for the extension movements of the shockabsorber according to the other example embodiments of the invention.

It is understood that the foregoing description is that of the preferredembodiments of the invention and that various changes and modificationsmay be made thereto without departing from the spirit and scope of theinvention as defined in the appended claims.

LIST OF REFERENCE NUMERALS

-   1 shock absorber-   2 shock absorber cylinder-   3 damping volume-   4 damping fluid-   5 shock absorber piston-   6 piston rod-   7 retraction direction of the shock absorber-   8 damping opening-   9 compensation volume reservoir-   10 compensation piston-   11 entry opening-   12 exit opening-   13 ascending pipe-   14 compression stage-   15 stage throttle-   16 disk valve-   17 valve disk-   18 valve shaft-   19 closing direction of the disk valve-   20 valve disk pressure surface-   21 disk valve seat-   22 entry edge of the disk valve seat-   23 protrusion-   24 analogue piston-   25 analogue piston pressure surface-   26 pressure channel-   27 analogue piston counter surface-   28 counter channel-   29 first piston head-   30 second piston head-   31 first chamber-   32 second chamber-   33 connection recess-   34 piston shaft-   35 gas spring-   36 gas-   37 damping fluid seal-   38 gas seal-   39 access channel-   40 pipe piece-   41 tilt seal-   42 pressure adjustment screw-   43 biasing spring-   44 damping fluid channel-   45 cross-section reduction-   46 back flow valve-   47 back flow bypass-   48 extra spring-   49 stop-   50 non-return valve-   51 seat ring-   52 non-return valve seat-   53 rebound stage-   54 support seat-   55 valve disk piston surface-   56 hollow cylinder-   57 piston stump-   58 time axis-   59 end of time duration-   60 excitation amplitude of the stroke excitation-   61 stroke excitation of desired damping strut movement-   62 stroke excitation of undesired damping strut movement-   63 stroke excitation maximum-   64 range of stroke maxima at obstacles-   65 excitation duration of stroke excitation-   66 stroke excitation by curbstone edge-   67 stroke excitation by low stone-   68 stroke excitation by breaking process-   69 stroke excitation by pedalling-   70 damping force curve at stroke excitation 66 by curbstone edge-   71 damping force curve at stroke excitation 67 by low stone-   72 damping force curve at stroke excitation 68 by breaking process-   73 damping force curve at stroke excitation 69 by pedalling-   74 retraction stroke-   75 damping force

What is claimed is:
 1. A movement stage for a hydraulic shock absorbercomprising: a damping volume filled with an incompressible dampingfluid; a stage throttle having a disk valve with a valve disk, ananalogue piston, and an elastic biasing means configured for biasing thevalve disk in a closing direction of the disk valve; said stage throttlebeing arranged so that the incompressible damping fluid flows throughsaid stage throttle in a direction opposite to the closing direction ofthe disk valve as the hydraulic shock absorber moves in at least onemovement direction; said valve disk being configured to generate a shockabsorber resistance force; said stage throttle being supported on theanalogue piston and on a support seat of the movement stage; saidanalogue piston having an analogue piston pressure surface arranged toface away from a biasing means; said valve disk having a valve diskpressure surface and a valve disk piston surface; said valve diskpressure surface being a portion of a surface of the valve disk that isarranged upstream of an entry edge of a disk valve seat; said valve diskpiston surface being arranged to face away from said valve disk pressuresurface; said valve disk pressure surface, said valve disk pistonsurface, and said analogue piston pressure surface being impinged by theincompressible damping fluid that flows out of the damping volume as thehydraulic shock absorber moves in the at least one movement direction;said biasing means being coupled with the disk valve via the analoguepiston and via the incompressible damping fluid impinged on the valvedisk piston surface; said valve disk piston surface being larger thansaid valve disk pressure surface when projected in the closing directionof the disk valve; and, said analogue piston moving towards the biasingmeans thereby increasing a bias force of the valve disk as the hydraulicshock absorber moves in the at least one movement direction.
 2. Themovement stage according to claim 1, wherein the valve disk pistonsurface is up to four times larger than the valve disk pressure surfacewhen projected in the closing direction of the disk valve.
 3. Themovement stage according to claim 1, wherein the analogue pistonpressure surface and the valve disk piston surface are equally largewhen projected in the closing direction of the disk valve.
 4. Themovement stage according to claim 1, wherein the analogue pistonpressure surface is larger than or smaller than the valve disk pistonsurface when projected in the closing direction of the disk valve. 5.The movement stage according to claim 1, wherein the analogue piston hasan analogue piston counter surface facing away from the analogue pistonpressure surface and being impinged by the incompressible damping fluidthat has already passed the disk valve seat as the hydraulic shockabsorber moves in the at least one movement direction.
 6. The movementstage according to claim 5, wherein the analogue piston pressure surfaceand the analogue piston counter surface are equally large when projectedin the closing direction of the disk valve.
 7. The movement stageaccording to claim 1, wherein the elastic biasing means is arrangedbetween the analogue piston and the support seat to spatially isolatethe elastic biasing means from the incompressible damping fluid that hasnot yet passed the disk valve seat as the hydraulic shock absorber movesin the at least one movement direction.
 8. The movement stage accordingto claim 1, wherein the analogue piston is arranged in a hollow cylinderin a displaceable manner, and wherein the analogue piston is sealed by adamping fluid seal.
 9. The movement stage according to claim 1, whereinthe analogue piston is configured to move to a first extreme position atwhich the bias force, that is transferred from the analogue piston viathe incompressible damping fluid to the valve disk piston surface, iszero.
 10. The movement stage according to claim 8, wherein the analoguepiston is configured to move to a second extreme position at which thebias force, that is transferred from the biasing means via the analoguepiston and via the incompressible damping fluid to the valve disk pistonsurface on the valve disk, has a maximum value.
 11. The movement stageaccording to claim 10, wherein the damping fluid seal generates afriction force as the analogue piston moves from a first extremeposition to the second extreme position, and wherein the friction force,that is transferred via the analogue piston and via the incompressibledamping fluid impinged on the valve disk piston surface, increases thebias force of the disk valve in the closing direction.
 12. The movementstage according to claim 8, wherein the disk valve has a piston stump,wherein the valve disk is arranged on an outside of the piston stump,wherein the valve disk piston surface is arranged on a front side of thepiston stump, wherein the hollow cylinder is confined on a side of theanalogue piston pressure surface of the analogue piston by the pistonstump in the displaceable manner, and wherein the hollow cylinder isconfined on the side of an analogue piston counter surface by an innerside of the support seat, on which the biasing means is supported. 13.The movement stage according to claim 1, further comprising: anon-return valve having the closing direction opposite to the closingdirection of the disk valve; a seat ring being concentrically arrangedaround a piston stump, said disk valve seat being arranged on a frontside of the seat ring and said non-return valve seat being arranged onthe other side of the seat ring so that the non-return valve is closedas the disk valve is open and the non-return valve is open as the diskvalve is closed, whereby the non-return valve acts as a counter stagethrottle to the stage throttle.
 14. The movement stage according toclaim 1, wherein the biasing means is a coil spring.
 15. The movementstage according to claim 1, wherein the biasing means is a gas spring.16. The movement stage according to claim 15, further comprising achamber between the analogue piston and the support seat, wherein thechamber is filled with a gas, wherein the support seat has a shape of aring, wherein the analogue piston has a piston shaft that extendsthrough the opening of a protrusion and that is arranged on theprotrusion in a gas sealed manner.
 17. The movement stage according toclaim 15, wherein the analogue piston includes a first piston head and asecond piston head held in a distance relative to one another by apiston shaft, wherein the support seat is arranged between the first andsecond piston heads so that a first chamber and a second chamber aredefined by the first and second piston heads and the support seat, andwherein the first and second chambers are filled with a gas.
 18. Themovement stage according to claim 17, wherein the piston shaft includesa connection recess, and wherein a gas pressure equalizes in the firstand second chambers via the connection recess when the analogue pistonis at a position at which the support seat is positioned next to theconnection recess so that the first and second chambers are connectedwith one another in a gas conductive manner.
 19. The movement stageaccording to claim 1, wherein a center of mass of the analogue pistonpressure surface coincides with the center of mass of the valve diskpressure surface when the center of mass of the analogue piston pressuresurface is projected in the closing direction of the disk valve on thevalve disk pressure surface.
 20. The movement stage according to claim1, wherein a center of mass of the analogue piston pressure surface isshifted with respect to the center of mass of the valve disk pressuresurface when the center of mass of the analogue piston pressure surfaceis projected in the closing direction of the disk valve on the valvedisk pressure surface.
 21. The movement stage according to claim 1,wherein the closing direction of the disk valve and a movement directionof the analogue piston enclose an angle that is smaller than 180°.